CN1033337C - Swirling-flow burner - Google Patents
Swirling-flow burner Download PDFInfo
- Publication number
- CN1033337C CN1033337C CN92114838A CN92114838A CN1033337C CN 1033337 C CN1033337 C CN 1033337C CN 92114838 A CN92114838 A CN 92114838A CN 92114838 A CN92114838 A CN 92114838A CN 1033337 C CN1033337 C CN 1033337C
- Authority
- CN
- China
- Prior art keywords
- injector
- oxidant
- fuel
- gaseous
- combustion zone
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000007800 oxidant agent Substances 0.000 claims abstract description 54
- 239000002737 fuel gas Substances 0.000 claims abstract description 4
- 238000002485 combustion reaction Methods 0.000 claims description 54
- 230000001590 oxidative effect Effects 0.000 claims description 36
- 239000000446 fuel Substances 0.000 claims description 35
- 238000002347 injection Methods 0.000 claims description 14
- 239000007924 injection Substances 0.000 claims description 14
- 239000007921 spray Substances 0.000 claims description 12
- 239000007789 gas Substances 0.000 claims description 7
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000000034 method Methods 0.000 claims description 3
- 230000003197 catalytic effect Effects 0.000 claims description 2
- 235000013351 cheese Nutrition 0.000 claims 1
- 230000003068 static effect Effects 0.000 abstract 1
- 239000003054 catalyst Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000011261 inert gas Substances 0.000 description 2
- 230000014759 maintenance of location Effects 0.000 description 2
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
- F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
- F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pre-Mixing And Non-Premixing Gas Burner (AREA)
- Gas Burners (AREA)
- Control Of Combustion (AREA)
- Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
- Manufacture, Treatment Of Glass Fibers (AREA)
Abstract
Swirling-flow burner with improved design comprising U-shaped oxidizer and fuel gas injectors arranged coaxially at the burner face. The burner is further equipped with a bluff-body with static swirler blades extending inside the oxidizer injector.
Description
The present invention relates to a kind of be used for the gas fuel combustion reactor have separately fuel and the turbulent burner of oxidant feedway.
This class burner is mainly used in the burning of gas combustion industrial furnace and flow process heater, and this kind equipment need have the retention flame of heats of combustion intensity.Usually the turbulent burner of structure comprises a spray combustion pipe that has fuel backbone pipe, and an oxidant supply port surrounds this fuel backbone pipe.Fuel and oxidant obtain by the oxidant by cyclone in the abundant mixing of combustion zone, and cyclone is installed in burner surface place on the central tube.Therefore, oxidant flows in the mode of eddy flow, thereby the inside and outside height recirculation that forms combustion product produces high combustion heat intensity.
The shortcoming of the common turbulent burner of said structure is, the surface of burner (this be have the industrial furnace of this structure desired) under the air-flow high flow rate, and to cause that burner surface is subjected to overheated because of the height interior recirculation along the combustion zone central axis.Therefore, hot combustion product returns flowing of burner surface, causes burner surface to be heated to high temperature rapidly and consequently is damaged.
General purpose of the present invention is by improving the combustion front structure of this known turbulent burner, to overcome above-mentioned defective.
According to the observation, this improvement structure is based on observed such fact: when forming a kind of oxidant eddy flow its total flow direction is concentrated along the combustion zone axis, and in the identical time, when gaseous fuel flows to same axis, just can obtain a kind of retention flame, and can not produce the harmful interior recirculation of hot combustion product with heats of combustion intensity.
According to this observation, turbulent burner of the present invention comprises: spray combustion pipe and one coaxial and fire the central oxidizer supply pipe that pipe separates with spray, thus, between two pipes, formed an annular gas fuel channel, oxidant supply pipe and fuel gas passage have the independent entrance point and the port of export, wherein:
The port of export of gaseous-fuel injector and gas burning gallery links, and this gaseous-fuel injector has a U-shaped cross section inner surface around spray combustion pipe and injector common axis;
The port of export of oxidizer injector and oxidant supply pipe is connected, and this oxidizer injector has one and gaseous-fuel injector is coaxial and the U-shaped cross-section that separates;
A gaseous fuel jet chamber that between gaseous fuel and oxidizer injector surface, forms;
An oxidant injection chamber that in the oxidizer injector surface, forms;
Each jet chamber all has a channel section, and is provided with a ring exit end around common axis;
A columniform bluff, it is indoor to be co-axially mounted on oxidant injection, and this bluff has a dome-type upstream extremity and a taper downstream; And
A cyclone is installed on the bluff, and between its upstream extremity and downstream, this cyclone has one group of quiet swirl vane that extends to the oxidant injection chamber surface;
Therefore, deliver to the oxidant of oxidant injection chamber, under the acting in conjunction of bluff and cyclone, be ejected into the combustion zone, downstream with cyclone mode, this oxidant stream flows by the common axis around jet chamber and combustion zone after the oxidant injection chamber;
Oxidant mixes in the fuel region with the gaseous fuel of delivering to the gaseous fuel jet chamber, and sprays into combustion zone in the mode that flows in axial towards the combustion zone after passing gaseous-fuel injector.
The eddy flow that cyclone induces helps by increasing the mixing that contact area promotes gaseous fuel and oxidant.Between the inclination angle of swirler blades is adjusted in 15 ° and 75 ° of scopes, and preferably between 20 ° and 45 ° the time, can obtain to mix effectively.
Simultaneously, the mobile graphic that inwardly flows along the combustion zone axis that is caused by jet chamber's channel section has avoided that if not hot combustion product, will cause burner surface overheated around the recirculation of combustion zone axis in the high-temperature area.
In addition, this inside mobile graphic also can cause the height external recirculation of low temperature perimeter, combustion zone.Only there is chilled combustion product to backflow from this zone and gets back to burner surface, among this part combustion product of this surface is inhaled into hot combustion zone again, and heating once more there.
When burner of the present invention was used for the gas combustion reactor, the recirculation flow of chilled combustion product had advantageously prevented to have prolonged the life-span of reactor around the be heated impact of combustion product of the reactor wall of combustion zone.
Can form the sharp-edged that have minimum wedge angle by oxidizer injector and further reduce near the temperature of the burner surface of jet chamber's port of export oxidant injection chamber outlet end place.The minimizing of being heated of injector and suitably the acquisition of mechanical strength can be between 15 ° and 65 ° the time at wedge angle, obtain when being preferably between 15 ° and 40 °.
Another advantage of burner of the present invention is that the combustion product height external recirculation of cooling has formed the even temperature distribution at the burning outlet area.
This duration of work at the combustion-type hydrogen-catalyst reactor is very important, and its output depends on the Temperature Distribution in the catalyst bed that typically is arranged on the burning outlet area to a great extent.
Therefore, burner of the present invention is particularly suitable for being used in the heating in the gaseous fuel reactor and finishes catalytic process.
Above-mentioned purpose of the present invention and advantage thereof will be done to describe further with reference to accompanying drawing hereinafter, and wherein, unique accompanying drawing is represented the cross sectional representation according to a kind of turbulent burner of a specific embodiment of the present invention.
In the drawings, spray combustion pipe 2 coaxially around a central oxidizer supply pipe 4, forms gaseous fuel feed path 6 with respect to common axis 16 between two pipes.
The cross section that injector 10 has around axis 16 is the inner surface of U-shaped, and this injector 10 is installed in the port of export 8 places of spray combustion pipe 2.Injector 10 holds the injector 12 of a coaxial setting, and this injector 12 has U-shaped cross-section and is installed on the port of export 14 of central tube 4.
The U-shaped shape of injector can have the suitable metal body of column part and tapered segment and acquisition easily by processing.The best value of transition angle between cylinder and the conical part is within 115 ° and 170 ° of scopes.
Injector 10 and 12 surface surround the gas combustion jet chamber 18 that communicates with gaseous fuel feed path 6 and the oxidant injection chamber 20 within the injector 12 of central tube 4 ports of export.Jet chamber 18 and 20 has the channel section around axis 16, and its round exit end 22 and 24 is arranged to axis 16 coaxial.The port of export 24 of jet chamber 20 can lead to the bottom of jet chamber 18.
Edge round the injector 12 of oxidant injection chamber outlet end is taper, and has minimum wedge angle γ, and is overheated to prevent this edge, will describe in detail hereinafter about this point.
Jet chamber 20 also be equipped with one with the coaxial cylindrical bluff 26 that separates of these chamber 20 inner surfaces.Bluff 26 has dome-type upstream extremity 28 and taper downstream 30.Round the periphery of bluff 26 cyclone 32 has been installed, cyclone 32 has one group of quiet swirl vane (not shown), and these quiet swirl vanes extend to the surface of jet chamber 20.
When having the burner operation of said structure, gaseous fuel is fed in the jet chamber 18 by passage 6, and the combustion zone in 20 ports of export, 24 downstreams, spirt jet chamber.By the channel section of jet chamber 18, inject the gaseous fuel flow of combustion zone, towards the jet chamber 18 and the direction of the common axis 16 of combustion zone flow, shown in arrow among the figure.In the combustion zone, gaseous fuel flow and the oxidant that is fed in the central tube 4 mix, and 20 are ejected into the combustion zone through the jet chamber.
Before being ejected into the combustion zone, oxidant stream has formed eddy flow through the passage of cyclone 32, and by the channel section of bluff 26 and jet chamber 20, the eddy flow oxidant is arranged into combustion zone with total flow tendency of enclosing the combustion zone axis.
As a result, the mixing of oxidant and gaseous fuel flow is mainly finished in combustion zone axis temperature province on every side.Therefore, prevented harmful interior recirculation of the hot combustion product in this zone.Recirculation only is formed on the low temperature perimeter of combustion zone, like this, has reduced the material temperature near jet chamber's port of export.As above-mentioned, temperature in this zone can be further controlled by the angle γ round the oxidizer injector edge of the port of export of oxidant injection chamber, like this, the Mixed Zone of oxidant and gaseous fuel can be remained on apart from edge larger distance place by the way that reduces the wedge angle angle.
By the reference specific embodiment the present invention is described,, clearly, can easily makes various alternatively changes, will not exceed scope of the present invention for those those skilled in the art.For example; application scenario in the very high combustion heat intensity of needs; burner surface can be by the passage that gets out in oxidizer injector 12; be protected in the edge introducing jet chamber 18 of this injector 12 and a kind of inert gas or the inert gas flow in 20 port of export zones, prevent to be subjected to high temperature.
Claims (6)
1. turbulent burner, comprise: a spray combustion pipe, coaxial with this spray combustion pipe and separate a with it central oxidizer supply pipe forms an annular gas fuel channel between two pipes, this oxidant supply pipe and fuel gas passage have the independent entrance point and the port of export, it is characterized in that:
A gaseous-fuel injector that connects with the port of export of fuel gas passage, this gaseous-fuel injector have a U-shaped cross section inner surface around the common axis of this spray combustion pipe and injector;
An oxidizer injector that connects with the oxidant supply pipe port of export, this oxidizer injector have one and gaseous-fuel injector is coaxial and the U-shaped cross section surface that separates with it;
A gaseous fuel jet chamber that between gaseous fuel and oxidizer injector surface, forms;
An oxidant injection chamber that within the oxidizer injector surface, forms;
Each above-mentioned jet chamber all has channel section, and is provided with a ring exit end around common axis;
One is co-axially mounted on the indoor cylindrical bluff of oxidant injection, and this bluff has a cheese upstream extremity and a taper downstream; And
The cyclone between straight upstream extremity and downstream that is installed on the bluff; This cyclone has one group of quiet swirl vane that extends to the oxidant injection chamber surface;
Thus, by means of bluff and cyclone, the oxidant of delivering in the oxidant injection chamber sprays into combustion zone, downstream in the mode of eddy flow, and this oxidant stream is mobile around the common axis of above-mentioned jet chamber and combustion zone after passing the oxidant injection chamber;
Oxidant mixes with gaseous fuel in delivering to the gaseous fuel jet chamber mutually in the combustion zone, and sprays into combustion zone with the direction that inwardly flows towards the combustion zone axis after passing the gaseous fuel jet chamber.
2. turbulent burner according to claim 1, the inclination angle that it is characterized in that being installed in the swirl vane in the cyclone are 15 °-75 °.
3. turbulent burner according to claim 2, the inclination angle that it is characterized in that swirl vane are 20 °-45 °.
4. turbulent burner according to claim 1 is characterized in that oxidizer injector has a wedge angle at jet chamber's port of export place, and this wedge angle is 15 °-60 °.
5. turbulent burner according to claim 4, the wedge angle that it is characterized in that this oxidizer injector are 15 °-40 °.
6. according to the described turbulent burner of above-mentioned arbitrary claim, be used for carrying out catalytic process with the gaseous fuel reactor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK197491A DK168460B1 (en) | 1991-12-06 | 1991-12-06 | Swirl burner |
| DK1974/91 | 1991-12-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1074024A CN1074024A (en) | 1993-07-07 |
| CN1033337C true CN1033337C (en) | 1996-11-20 |
Family
ID=8109216
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN92114838A Expired - Lifetime CN1033337C (en) | 1991-12-06 | 1992-12-03 | Swirling-flow burner |
Country Status (15)
| Country | Link |
|---|---|
| US (1) | US5496170A (en) |
| EP (1) | EP0545440B1 (en) |
| JP (1) | JP3509888B2 (en) |
| CN (1) | CN1033337C (en) |
| AT (1) | ATE135811T1 (en) |
| AU (1) | AU655340B2 (en) |
| CA (1) | CA2084337C (en) |
| DE (1) | DE69209243T2 (en) |
| DK (1) | DK168460B1 (en) |
| ES (1) | ES2087410T3 (en) |
| NZ (1) | NZ245336A (en) |
| PL (1) | PL170438B1 (en) |
| RU (1) | RU2091668C1 (en) |
| UA (1) | UA26378C2 (en) |
| ZA (1) | ZA929431B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425793A (en) * | 2011-10-19 | 2012-04-25 | 中国科学院广州能源研究所 | Self-backheating swirling burner for fuel gas with low heat value |
| CN108603663A (en) * | 2016-02-09 | 2018-09-28 | 索拉透平公司 | Fuel injector and method of engine operation for internal-combustion engine system |
Families Citing this family (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5149263A (en) * | 1991-06-06 | 1992-09-22 | Bowles Fluidics Corporation | Torch burner method and apparatus |
| US5390857A (en) * | 1994-06-01 | 1995-02-21 | Haldor Topsoe A/S | Gas injector nozzle |
| US5597298A (en) * | 1994-12-13 | 1997-01-28 | Praxair Technology, Inc. | Laminar flow burner |
| US8979525B2 (en) | 1997-11-10 | 2015-03-17 | Brambel Trading Internacional LDS | Streamlined body and combustion apparatus |
| DE19803879C1 (en) * | 1998-01-31 | 1999-08-26 | Mtu Muenchen Gmbh | Dual fuel burner |
| ATE341524T1 (en) * | 1998-02-17 | 2006-10-15 | Haldor Topsoe As | METHOD FOR AUTOTHERMAL STEAM REFORMING OF A HYDROCARBON FEED |
| ES2251205T3 (en) * | 1998-07-02 | 2006-04-16 | Haldor Topsoe A/S | PROCEDURE FOR THE AUTOTHERMAL REFORMATION OF A HYDROCARBONATED LOAD. |
| US6058855A (en) * | 1998-07-20 | 2000-05-09 | D. B. Riley, Inc. | Low emission U-fired boiler combustion system |
| EP0987492B1 (en) * | 1998-09-15 | 2003-05-28 | Haldor Topsoe A/S | Process for the combustion of hydrocarbon fuel in a burner |
| DK173897B1 (en) | 1998-09-25 | 2002-02-04 | Topsoe Haldor As | Process for autothermal reforming of a hydrocarbon feed containing higher hydrocarbons |
| AU764286B2 (en) * | 1998-12-24 | 2003-08-14 | Luminis Pty Limited | Fluid mixing device |
| AUPP793698A0 (en) * | 1998-12-24 | 1999-01-28 | Luminis Pty Limited | Device to provide fluid mixing which is sensitive to direction and speed of external flows |
| US6351939B1 (en) * | 2000-04-21 | 2002-03-05 | The Boeing Company | Swirling, impinging sheet injector |
| DE50111599D1 (en) * | 2000-11-27 | 2007-01-18 | Linde Ag | PROCESS FOR THE CHEMICAL IMPLEMENTATION OF TWO GAS FLOWS |
| EP1221572B1 (en) | 2001-01-04 | 2005-10-05 | Haldor Topsoe A/S | Swirler burner |
| US7736501B2 (en) | 2002-09-19 | 2010-06-15 | Suncor Energy Inc. | System and process for concentrating hydrocarbons in a bitumen feed |
| CA2400258C (en) | 2002-09-19 | 2005-01-11 | Suncor Energy Inc. | Bituminous froth inclined plate separator and hydrocarbon cyclone treatment process |
| DE10332860A1 (en) * | 2003-07-18 | 2005-02-10 | Linde Ag | Gas burner for separately supplied gases has burner head made of aluminum material in region of output end of gas input channel |
| US20080271376A1 (en) * | 2007-05-01 | 2008-11-06 | General Electric Company | Fuel reformer system and a method for operating the same |
| EP2107301B1 (en) * | 2008-04-01 | 2016-01-06 | Siemens Aktiengesellschaft | Gas injection in a burner |
| US20100175386A1 (en) * | 2009-01-09 | 2010-07-15 | General Electric Company | Premixed partial oxidation syngas generation and gas turbine system |
| US20100175379A1 (en) * | 2009-01-09 | 2010-07-15 | General Electric Company | Pre-mix catalytic partial oxidation fuel reformer for staged and reheat gas turbine systems |
| DE102009010274B4 (en) | 2009-02-24 | 2014-06-18 | Eisenmann Ag | Burner for a thermal post-combustion device |
| CA2689021C (en) | 2009-12-23 | 2015-03-03 | Thomas Charles Hann | Apparatus and method for regulating flow through a pumpbox |
| CN103782099B (en) * | 2011-02-16 | 2016-03-16 | 气体产品与化学公司 | The oxygen enrichment of premixed air-gas burner |
| CN102401379B (en) * | 2011-11-11 | 2014-03-26 | 无锡市莱达热工工程有限公司 | Hot gas flat flame burner |
| US9285120B2 (en) | 2012-10-06 | 2016-03-15 | Coorstek, Inc. | Igniter shield device and methods associated therewith |
| EP2811228B1 (en) | 2013-06-07 | 2019-08-07 | Haldor Topsøe A/S | Burner |
| EP2821699A1 (en) * | 2013-07-02 | 2015-01-07 | Haldor Topsøe A/S | Mixing of recycle gas with fuel gas to a burner |
| DE102014116411B4 (en) * | 2014-11-11 | 2024-05-29 | Choren Industrietechnik GmbH | Swirl body and burner with swirl body and method for producing the swirl body |
| ES2708984A1 (en) | 2017-09-22 | 2019-04-12 | Haldor Topsoe As | Burner for a catalytic reactor with slurry coating with high resistance to disintegration in metal powder (Machine-translation by Google Translate, not legally binding) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US903736A (en) * | 1907-08-15 | 1908-11-10 | Alva D Lee | Oil-burner. |
| US1404429A (en) * | 1918-03-14 | 1922-01-24 | Tate Jones & Co Inc | Hydrocarbon blast burner |
| US1460130A (en) * | 1919-10-10 | 1923-06-26 | George W Hofmann | Liquid-fuel burner |
| US1763387A (en) * | 1926-04-06 | 1930-06-10 | Ryan Scully & Company | Oil burner |
| US2772729A (en) * | 1951-05-03 | 1956-12-04 | Hydrocarbon Research Inc | Apparatus for combustion of hydrocarbons |
| US3685741A (en) * | 1970-07-16 | 1972-08-22 | Parker Hannifin Corp | Fuel injection nozzle |
| DE2133126A1 (en) * | 1971-07-02 | 1973-01-11 | Zenkner Kurt Dr Ing | ACCORDING TO THE PRESSURE ATOMIZATION PRINCIPLE OF OIL BURNERS |
| FR2235274B1 (en) * | 1973-06-28 | 1976-09-17 | Snecma | |
| US3980233A (en) * | 1974-10-07 | 1976-09-14 | Parker-Hannifin Corporation | Air-atomizing fuel nozzle |
| US4139157A (en) * | 1976-09-02 | 1979-02-13 | Parker-Hannifin Corporation | Dual air-blast fuel nozzle |
| US4443228A (en) * | 1982-06-29 | 1984-04-17 | Texaco Inc. | Partial oxidation burner |
| US5020329A (en) * | 1984-12-20 | 1991-06-04 | General Electric Company | Fuel delivery system |
| US4773596A (en) * | 1987-04-06 | 1988-09-27 | United Technologies Corporation | Airblast fuel injector |
| US5014918A (en) * | 1989-04-12 | 1991-05-14 | Fuel Systems Textron Inc. | Airblast fuel injector |
-
1991
- 1991-12-06 DK DK197491A patent/DK168460B1/en not_active IP Right Cessation
-
1992
- 1992-12-02 CA CA002084337A patent/CA2084337C/en not_active Expired - Lifetime
- 1992-12-02 NZ NZ245336A patent/NZ245336A/en not_active IP Right Cessation
- 1992-12-03 CN CN92114838A patent/CN1033337C/en not_active Expired - Lifetime
- 1992-12-03 JP JP32431292A patent/JP3509888B2/en not_active Expired - Lifetime
- 1992-12-04 AT AT92120754T patent/ATE135811T1/en active
- 1992-12-04 DE DE69209243T patent/DE69209243T2/en not_active Expired - Lifetime
- 1992-12-04 RU RU9292004523A patent/RU2091668C1/en active
- 1992-12-04 ZA ZA929431A patent/ZA929431B/en unknown
- 1992-12-04 EP EP92120754A patent/EP0545440B1/en not_active Expired - Lifetime
- 1992-12-04 PL PL92296849A patent/PL170438B1/en unknown
- 1992-12-04 ES ES92120754T patent/ES2087410T3/en not_active Expired - Lifetime
- 1992-12-04 AU AU29917/92A patent/AU655340B2/en not_active Expired
-
1993
- 1993-05-12 UA UA93002779A patent/UA26378C2/en unknown
-
1994
- 1994-07-08 US US08/309,346 patent/US5496170A/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425793A (en) * | 2011-10-19 | 2012-04-25 | 中国科学院广州能源研究所 | Self-backheating swirling burner for fuel gas with low heat value |
| CN108603663A (en) * | 2016-02-09 | 2018-09-28 | 索拉透平公司 | Fuel injector and method of engine operation for internal-combustion engine system |
Also Published As
| Publication number | Publication date |
|---|---|
| US5496170A (en) | 1996-03-05 |
| EP0545440B1 (en) | 1996-03-20 |
| ZA929431B (en) | 1993-05-28 |
| EP0545440A2 (en) | 1993-06-09 |
| ES2087410T3 (en) | 1996-07-16 |
| CA2084337C (en) | 1998-06-23 |
| DK168460B1 (en) | 1994-03-28 |
| AU2991792A (en) | 1993-06-10 |
| CA2084337A1 (en) | 1993-06-07 |
| UA26378C2 (en) | 1999-08-30 |
| DK197491D0 (en) | 1991-12-06 |
| RU2091668C1 (en) | 1997-09-27 |
| NZ245336A (en) | 1994-10-26 |
| JP3509888B2 (en) | 2004-03-22 |
| JPH05256420A (en) | 1993-10-05 |
| CN1074024A (en) | 1993-07-07 |
| DE69209243D1 (en) | 1996-04-25 |
| EP0545440A3 (en) | 1993-08-04 |
| AU655340B2 (en) | 1994-12-15 |
| DE69209243T2 (en) | 1996-07-25 |
| ATE135811T1 (en) | 1996-04-15 |
| DK197491A (en) | 1993-06-07 |
| PL296849A1 (en) | 1993-07-26 |
| PL170438B1 (en) | 1996-12-31 |
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